Auxiliary power-transmitting apparatus for tractors



C. W. MOTT May 11, 195E AUXILIARY POWER TRANSMITTING APPARATUS FOR TRACTORS 4 Sheets-Sheet 1 Filed Sept. 10, 1945 May 1, 1951 c. w. MOTT 2,551,454

' AUXILIARY POWER TRANSMITTING APPARATUS FOR TRACTORS Filed Sept. 10, 1945 4 Sheets-Sheet 2 .57. veni a 7"" Car! M11055 C. W. MOTT May 1, 1951 AUXILIARY POWER TRANSMITTING APPARATUS FOR TRACTORS A 4 Sheets-Sheet 3 Filed Sept. 10, 1945 fnuenlz" Carl w. M055 iv P0. Q H' ULQ M y 1951 c. w. MOTT 2,551,454

AUXILIARY POWER TRANSMITTING APPARATUS FOR TRACTORS Filed Sept. 10, 1945 4 Sheets-Sheet 4 Patented May 1, 1951 AUXILIARY POWER- TRANSMITTING APPARATUS FOR TRACTOR/S Carl W. Mott, La Grange, Ill., assignor to International Harvester Company, a corporation of New Jersey Application September 10, 1945, Serial No. 615,329

3 Claims. (01. 74-.764)

This invention concerns power transmitting apparatus serviceable as a power lift for tractors and the like and relates particularly to a reversibly drivable gearing and a braking control for certain elements thereof for determining the direction of power transmission.

An object of this invention is the provision of an auxiliary power transmitting apparatus utilizing planetary gearing controllable by selectively applying braking force to brake drums thereof to cause a driven part of the apparatus to be driven in either of opposite directions from a constantly rotatable driving structure.

Another object is the provision of a planetary gearing arrangement wherein the drums brakable to incur opposite movement of the driven part are coaxial and adjacent and tend to rotate in opposite directions to adapt braking thereof by bands having anchored ends and free ends which are movable in opposite directions for Winding the bands onto the drums in the direction of drum rotation tendencies, whereby rotation of the drums supplements the application of each band by a control which is oppositely movable from a neutral position in which neither band is applied. The arrangement is one facilitating ease of operation manually whereby an operator can operate a finger-gripped lever for movement in opposite directions to obtain correlated movement of the driven part.

Another object is the provision of an auxiliary power transmitting apparatus employing planetary gearing for driving an internally threaded member in selectively opposite directions to advance or retract an exteriorly threaded member meshed with the internally threaded member and telescopic with a hollow driving structure, and a casing havin a bearing for a cross head constrained for advancement and retraction with the exteriorly threaded member.

Another object is the provision of a floating lever assembly by means of which controlling movement is applied to the brake drum bands both manually and by virtue of the resulting movement of the driven part of the apparatus to release each band and thereby cause cessation of movement of said driven part when it is advanced or retracted an amount correlated with the amount of advance or retraction of a manual control.

Another object is the provision of a novel arrangement of auxiliary power transmitting apparatus mounted upon the body of a tractor rearwardly of a clutch centaining compartment thereof and employing separately engine-driven z components which receive power from the .en gine through a shaft geared to a part rotatable with the driven part of the clutch within such housing and extending rearwardly exteriorly of the tractor body into mutual dliVing relation with said components.

A further object is the provision of a novel eccentrically mounted bearing for the aforesaid rearwardly extending shaft for displacing the front end of the shaft to control the meshed or demeshed relation thereof with respect to a driving gear therefor in the clutch compartment incident to flexing the shaft pursuant to incurrin such lateral displacement.

Still a further object is the provision of a new form of brake band having a substantially cylindrical formation in its relaxed condition and disposed within a cylindrical portion of the power transmission apparatus casing to limit the extension of such band, together with anchorage means for an end of the band and means for displacing the other end of the band circumferentially to contract the same onto a, brake drum of the apparatus.

Still another object of the invention is the pro.- vision of a new generally cylindrical plural convolution brake band formed from a cylindrical member having notches in opposite end portions at circumferentially separate positions to leave an intervening portion of the member between such notches and having a circumferential groove extending around the member between the bottoms of the notches oppositely from the intervening portion.

These and other desirable objects inherent and encompassed by the invention will be more fully comprehended upon reading the ensuing description with reference to the drawings, wherein:

Fig. l is a side elevational view of an auxiliary power transmitting apparatus embodying a preferred form of the invention, the apparatus being illustrated upon the body of a tractor which is shown fragmentarily in side elevation with parts of the body broken away at the clutch com partment to disclose the driving connection between a clutch mounted gear and the apparatus.

Fig. 2 is a plan view of the apparatus shown in Fig. 1;

Fig. 3 is a vertical sectional view taken axially through one of the gearing components of the apparatus as indicated by the line 3-3 in Fig. 5;

Fig. 4 is a sectional view taken through a spring chamber formed integrally with a control lever of the apparatus, the view being taken on the line 4-'--4 of Fig. 5;

Fig. is a vertical sectional view taken transversely through the unit A substantially on the line 55 of Fig. 3;

Fig. 6 is a sectional view taken on the line 5-5 of Fig. 5 for showing a portion of the control linkage of the apparatus;

Fig. 7 is a horizontal plan view of the main casing portion of one of the gearing components of the apparatus with an auxiliary portion of the casing removed of exposing brake bands which control brake drums of planetary gearing within the casing; and

Fig. 8 is an elevational View looking radially of a brake band of an improved type employed in the apparatus.

The power transmitting apparatus herein disclosed embodies two identical units A and B, each having a casing Ca mounted on a body H of a wheel tractor. Said tractor has rear rubber tire carrying traction wheels I2 rotatable about an axis X. The Wheels |2 are conventionally driven from an engine E through a clutch C, a clutch driven shaft (not shown) extending rearwardly from the clutch through the hollow body ll, change-speed gearing (not shown) within a gearing compartment l3 forming the rear end of the body H, and the usual differential gearing driven from the tail shaft of the transmission.

Power is transmitted to each unit A and B of the auxiliary power transmitting apparatus from a gear I 4 in the clutch containing compartment I5 and which is mounted on and is constrained for rotation with the clutch casing l6 which rotates constantly with the engine crank shaft. Power from the gear I4 reaches the apparatus through a companion gear I 1, a shaft l8 constrained for rotation with the gear IT, a gear l9, Fig. 2, constrained for rotation with the rear end of the shaft I8, and driving gears 2| of each of the units A and B that mutually mesh with said gear l9.

Two units, A and B, are employed in the present installation for respectively operating concentric rockshafts 22 and 23, Figs. 1 and 2. Rockshaft '23 has sleeve portions 24 and 25, Fig. 2, joined by a bridge portion 26 and spaced at opposed ends for receiving a collar 21 which is constrained for rotation with the inner of said shafts, 22. Rock-shaft 23 is pivotally carried in bearings 28 at opposite sides of the tractor body II and which bearings are formed in upper end portions of arms 29 of a bracket secured to the tractor body. Rock-shaft arms 3| for the attachment of implement operating rods or the like are constrained for rotation with the inner rock-shaft 22 while similar arms 32 are constrained for rotation with the outer sleevelike shaft structure 23. Unit A has a cross-head 33, Fig. 3, for pivoting the rock-shaft structure 22 through a connecting rod 34, the front end of which is connected by a pin 35 with a bifurcated arm structure 36 integral with the collar 21 which is fixed for rotation with said shaft. A similar cross-head (not shown) in a cross-head guide bearing 3'! of unit B is connected by a connected rod 34 with a bifurcated arm structure 38 on the rock-shaft structure 23 for pivoting this structure pursuant to fore and aft movement of said cross-head in its guide bearing.

Since the two units A and B are identical, a detail construction of the unit A will suffice for both. Referring therefore to the unit A illustrated in Figs. 3 to 8, the casing Ca of this unit will be seen to have a lower main portion 39 shown in Figs. 3 and 5 in coaxial relation with planetary gearing contained therein. An upper portion 4| of the casing for containing and supporting controls for the planetary gearing is communicative with the main portion of the casing through an intermediate sheet-like casing portion or part 42 assembled between the portions or parts 39 and 4|. The cross-head guide hearing 31 is formed integrally with a front end casting 43 of the casing. This front end casting has an apertured ear 44 which together with an apertured ear 45 on the main part of the casing serves as attaching means receivable of cap screws 46, Fig. 1, for securing the casing to the tractor body The back end of the casing main portion is closed by an end casting 41. Casting 47 covers the back ends of casings in both units A and B, as illustrated in Fig. 2, and also serves to enclose the two gears 2| and the driving gear l9 therefor. A bearing 48 on the front wall of casting 41 between the units A and B journals the rear end portion of the drive shaft l8.

A driving structure 49 of the power transmitting unit A includes the gear 2| of such unit and a tubular member 5| having such gear 2| keyed to a rear end portion thereof as indicated at 50. This tubular member is journaled in a bushing 52 supported in a rear wall 53 of the casing, and a front end portion of said tubular member is carried by a bushing 54 of a planetary gear carrier hub 55 which is mounted on an internally threaded member 56. A splined connection 51 exists between the parts 55 and 56, and said parts 56 is journaled coaxially of the casing by the inner race of a ball bearing unit 58.

Sun gear means for each of two planetary gear units 59 and El is provided by gear teeth 62 formed integrally with the tubular member 5|. The first of said planetary gear units, 59, comprises a planet gear carrier 63 journaled on the tubular member 5| by a bushing 64. Carrier 63 has three circumferentially spaced planet gear shafts 65 upon which planet gears 66 are respectively journaled. A ring gear 61 of the planetary unit 59 is secured to the carrier 68 of the second planetary unit 6| by circumferentially spaced macnine screws 69. As explained above, the hub 55 of this carrier 68 is splined at 5'! to the internally threaded driven member 56.

When a brake drum formed integrally with the planet carrier 63 is constrained against rotation by a brake band 12, later to be explained in detail, the clockwise rotating driving structure 49, as viewed axially of the apparatus from the front, will impart counter-clockwise rotation to the planet gears 66. Since the gears 66 cannot planetate when the carrier is so constrained by the brake band 12, these gears in rotating counter-clockwise about their individual axes will impart counter-clockwise rotation to the ring gear 6! and-to the carrier 68 and the internally threaded member 56. As can be seen in Fig. 3, the internally threaded member 56 is held against endwise movement by a snap ring 13 and an internally threaded ring 14 at opposite ends of the inner race of bearing unit 58. The bearing unit 58 is held against endwise displacement by the casing shoulder 15 and an annular plate '16 clamped between the main portion of the casing and the front end casting 43. Consequently the counter-clockwise rotated member 56 will advance an exteriorly threaded driven member I! meshed therewith, and itself constrained against rotation. forwardly. An enlarged front end portion 18 of the exteriorly threaded driven member 11 forms part of the crosshead 33.

Engagement of the brake band 12 with the brake drum ll always conditions the rear planetary gear unit 5i) for causing endwise forward movement of the cross-head 33 in the manner just described. The forward planetary gear unit BI is alternatively conditionable for causing the crosshead 33 to move endwise rearwardly. Such c nditioning of the planetary unit El is incurred by braking engagement of a brake band 19 with a brake drum Bi which carries a ring gear 32 of the unit 5|. Planetary gears 83 of the unit 6-! are journaled upon spindles .84 anchored in the carrier 68. Planet gears 83 mesh mutually with the ring gear 82 and a portion of the sun gear means 62 so that When the drum 8| and the ring gear 82 are held against rotation, the clockwise rotating sun gear means 52, as viewed endwise from the front, will cause the planet gears to revolve in a clockwise direction at reduced speed about the principal axis of the unit. Thus the planet gear spindles 8 are correspondingly revolved and the carrier 68 is caused to rotate at the same reduced speed in a clockwise direction. Internally threaded member 55 rotates clockwise with the clockwise rotated carrier 63, thereby imparting endwise movement to the exteriorly threaded member H and to the crosshead 33 in an endwise rearward direction. Such rearward movement of the cross-head 53, incurred by application of the brake band 19 to the brake drum M for holding the latter stationary, acts through the connecting rod 34 and the arm structure 36, Figs. 1, 2, and 3, for pivoting the outer concentric rock-shaft structure 23 and the rock-shaft arms 32 to a clockwise limit a i]- lustrated in Fig. 1. Forward movement of the cross-head 33 by the engagement of the brake band '12 for holding the brake drum 7 I stationary will have the opposite efiect of rotating the rockshaft arms 32 in a counter-clockwise direction to a limit on the other side of the arms 3| with respect to which the arms 32 are illustrated in Fig. 1.

Each of the brake band #2 and 19 is constructed like the other. Brake band 19 is illustrated in Fig. 8. This brake band is formed from a perfectly cylindrical piece of stock material having notches 85 cut into opposite of its ends at circumferentially spaced positions for leaving an intervening portion 85 of the material. Following this operation the cylindrical band of material is out to form a slot 87 extending circumferentially of the piece oppositely from the intervening material 85 and communicatively with the bottoms of the notches 85. In this manner a brake band is formed which is truly cylindrical when in the relaxed condition. Slots 88 and 89 are formed in opposite end portions of the resulting band by suitable machine operations.

The mounting for brake band 79 is illustrated in Figs. 5 and '7. This band is disposed about the brake drum 8! and has the nctch 38 thereof disposed immediately beneath a hole 9! in the casing plate-like member 42. A cylindrical internal peripheral portion 92 of the casing registers radially with the brake band and is slightly smaller in diameter than the outer periphery of said band, whereby the band expands against the surface 92. Thus the surface 92 functions to support the released band 79 coaxially with the brake drum 8!. By this arrangement the released band 19 can be supported with its inner periphery extremely close to the outer periphery of the drum without actually touching the drum with any significant magnitude of pressure. Anchorage means for one end of the band i9 comprises a tiltable member 93 having a lower end portion 94 projecting into the slot 33 and an upper end portion 95 projecting into the opening 91, Fig. 7. Shoulders .96 adjacent to the upper end portion 95 of the til-table member 9.3 are adapted to abut against the under side of the plate-like member 42 for limiting upward movement of said member 93. Casing-mounted means manipulatable to regulate the tilt of the tiltable member 93 and hence the position of the anchorage end of said band 19 circumferentially of the drum 8| is in the form of a set screw 91.

The free end of the brake band 19 having the slot 89 therein is advanceable in a clockwise direction circumferentially of the drum Bl, as viewed in Fig. 5, for tightening the band upon the drum, while circumferential movement of the anchorage end of the band is prevented by the anchorage means 93-437. Such circumferential movement of the free end of the band is obtained by a lever arm 95 having an end portion projecting into the slot 39. Arm S8 is part of a lever .99 pivotable about an axis Y and supported upon trunnion members ltll, Fig. 6, at opposite ends. These trunnion members have threaded portions 1 02 screw threaded into the upper casing portion 4!. The means for controlling the pivoted position of the lever 99 will be presently described. ISaid lever has a second arm, I (it, for causing en:- gagement of the brake band 12 when such lever is rotated on the trunnions 5B! in the opposite direction to that above described for engaging the brake hand l9 with its drum '8 i.

In Fig. '7 the brake band 12 is illustrated as being similarly mounted as the band l9. However, the band 12 is disposedin the casing so that :its anchorage end, anchored to the casing by a tiltable member 9.3 corresponding to the member 83, is constrained against rotation in the Opposite circumferential direction. Anchorage member 93 cooperates with a set screw 91" corresponding to the set screw e"! in the manner hereinabove explained, while the unanchored end of the band i2 is movable circumferentially of the drum H by means of the lever arm I03 for tightening the band upon said drum. When the lever 99 is in the neutral position illustrated in Figs. 5, 6, and '7, neither of the brake bands 12 nor 19 is tightened upon its drum, whereby neither of the planetary units 58 nor 6! is condi tioned for causing driving force to be transmitted to the internally threaded member .56. Pivoting of the lever 99, as viewed in Fig. 5, in a counterclockwise direction will advance the free end of the band 19 for applying it to the brake drum BI and thereby conditioning the second planetary gearing unit, 6!, for rotating the internally threaded member 56 in the direction for moving the cross-head 33 .rearwardly, whereas clockwise rotation of the lever 99, as viewed in Fig. 5, will carry its arm Hi3 against the notch 89 therefor in the free end of the brake band H for applying this band in braking relation with the drum 7! to condition the planetary unit 59 for driving the internally threaded member 55 in the direction for moving the cross-head 33 forwardly.

Lever 99 is movable about its axis Y by means of an arm in the form of a pin its extending perpendicularly to the arms 93 and I03 and anchored in a socket H15 of such lever. The free end of the arm N14 is pivotally connected with an inter-2 mediate portion of a differential force-applying link I06. One end of the link I06 is pivotally connected at I01, Fig. 6, with a vertical link I08 which is pivotally connected at its upper end with an arm I99 which is constrained for rotation with a manually operated control shaft II I. The opposite end of the link I06 is pivotally connected with the lower end of a vertical link H2, and the upper end of this link is pivotally connected with an arm I I3 constrained for rotation with a tubular shaft H4 in which the manually operated shaft I II is mounted for rotation. Tubular shaft H4 is mounted for rotation in a casing bearing I I5 shown in Fig. 5. Tubular shaft I I4 has an arm II6 keyed thereto, and the free end of this arm is connected by a link In, Fig. 2, with a pivotal anchorage II8 on the rockshaft arm structure 36.

Clockwise rotation of the manual control shaft I I I, as viewed in Fig. 6, will force the right end of the link I06, Fig. 6, downwardly, and assuming the left end of this link I06 to be held against vertical movement by the linkage II2-I I3 etc., this lowering of the right end of said link I96 will lower the free end of the arm I 04 and thereby pivot the lever 99, Fig. 5, counter-clockwise for engaging the brake band I9 with the drum BI. In this manner the forward planetary gear unit BI is conditioned for driving the cross-head 33 rearwardly and thereby pivoting the rock-shaft arms 32 and 36 clockwise as viewed in Fig. 1. This clockwise pivoting of the rock-shaft arm structure 36 ensuing from the clockwise manual movement of the shaft III in Fig. 6 will incur rearward movement of the link II! of unit A and consequent rearward movement of the lower end of the arm I I6 (toward the observer as viewed in Fig. 5) and thereby cause clockwise rotation of the tubular shaft II4 as viewed in Fig. 6. This ensuing clockwise rotation of the tubular shaft II 4 will cause lifting of the left end of the link I06, as viewed in Fig. 6, and ultimate lifting of the mid-portion of the link I06 to the neutral position which it occupied prior to the manual clockwise rotation of the shaft III. When this neutral position of the mid-section of link I06 has been reattained, the lever 99 will be reestablished in its neutral position. The length of link H1, as well as the dimensions of the parts connected therewith for rotatin the sleeve shaft II4 from the rock-shaft arm structure 36, is so selected that the neutral position of the lever 99 for stopping further rearward movement of the crosshead and clockwise rotation of the arm structure 36, as viewed in Fig. 1, will occur when such movement attains a desired correlation with the amount of initiating manual movement imparted to the shaft II I.

Manual rotation of the shaft III counterclockwise, as viewed in Fig. 6, will raise the right end of the horizontal link I06 as well as the mid-section of this link and thereby cause clockwise rotation of the lever 99 as viewed in Fig. 5. As explained above, this counter-clockwise rotation of the lever 99 will incur engagement of the brake band 12 and condition the rear planetary unit 59 for moving the cross-head 33 forwardly and thereby pivoting the rock-shaft arm structure 36 counter-clockwise as viewed in Fig. 1. As a consequence of this counter-clockwise pivoting of the rock-shaft arm structure 36, the link In of unit A, as viewed in Fig. 1, will be moved forwardly and thereby impart movement of the arm II6, Fig. 5, for pivoting the tubular shaft II4, Fig. 6, counter-clockwise to lower the mid-portion of the link I06 and reestablish th neutral position of the lever 99 upon the rock-shaft arm structure 36 having pivoted counter-clockwise, as viewed in Fig. 1, a distance correlated with the amount of initiating manual movement imparted to the shaft III.

It is therefore the function of unit A of the apparatus to utilize power received from a constantly rotating engine-driven gear I4, Fig. 1, for selectively rotating the rock-shaft arm structure 3236 either clockwise or counter-clockwise, as viewed in Fig. 1, in variable amounts correlated with the clockwise or counter-clockwise rotation of a manually operated control shaft II I. Apparatus unit B has the same function with respect to rock-shaft arm structures 3I38 and operates identically in attaining this function.

Separate levers I2I are connected with the control shafts III of the auxiliary power-transmitting units A and B. lhese levers I2I and their connecting means with their respective shafts III are constructed similarly although these levers are faced oppositely endwise of said shafts so as to place knobs I22 on their upper ends so that their paths of movement are sufliciently contiguous that these knobs can be concurrently engaged by one hand of an operator for simultaneous movement. Levers I2I operate over quadrant straps I23 and I 24 secured at their rear ends to a bracket I25 which is mounted on the casing end casting 4?. The front ends of the quadrant straps I23 and I24 are clamped by a rivet I26 or the like against opposite ends of a tubular spacer member I27.

Referring now to the control lever I2I which is associated with the unit A, the means for connecting such lever with its manually controlled shaft III includes a spring chamber I 28, Figs. 4 and 5, formed integrally with the lower end of this lever. Bearings I29 in opposite walls of this spring chamber pivotally receive a reduced end section I3I of the shaft III. Between these opposite walls of the spring chamber a split ring I32 is fixed to said shaft end section I3I. Said ring I 32 has opposed apertured ears I33 which receive a key member I 34 therebatween which projects into an axial groove I 35 in the shaft section 3I. Dislodgment of the key from said groove is prevented by a cap screw I 38 turned into the apertured ears I33 and extending through a hole I31 in said key.

Split collar I32 has shoulders I38 and I39 for the abutment of legs MI and I42 of a bridge member I43. This bridge member has two spring guide stems I44 anchored therein and projecting upwardly in the spring chamber I28 through respective holes in a plate I45 held against a seat I46 by expansion springs I4? about the stems I44. Cotter keys I48 in the stems above the plate I45 enable the plate and the bridging member I43 to hold the springs captive on the guides I44 prior to the disposal of these parts within the chamber I28.

It is the purpose of the springs I41 to enable their associated lever IZI to be rotated relatively to their associated shaft III while these springs exert a force tending to rotate said shaft in the direction of rotative displacement of the lever. For example, if the lever I 2| and spring chamber I 28 illustrated in Figs. 4 and 5 were to be rotated clockwise as viewed in Fig. 4, the shaft III which initially resists rotation would remain relatively fixed while the end I4I of the bridging member I43 would be raised from the shoulder I38 and the end I 42 of said bridging member atoms;

would react on the shoulder I39 for compressing the springs and projecting the guide stems I44 upwardly through the plate I45. The pressure exerted by the springs through the bridge member end portion I42 onto the shoulder I39 would tend to rotate the shaft I I I also in the clockwise direction. This condition will prevail until the ensuing movement of the cross-head I33 causes movement of the differential link I for permitting the shaft III to rotate under the force imparted thereto by the compressed springs I 4-? and the diminution in their compression as the bridg i-ng upper end MI approaches its seat i38. Should the lever HI and its spring chamber I28 be rotated counter-clockwise as this chamber is viewed in Fig. 4, the bridge member end I42 would be lifted from its seat I39, while the end MI is urged against its seat I38 by the springs I I-I for yieldably urging the shaft Iii to pivot in the direction of pivoting ofthe lever. The sprigns Id-"I would then remain so additionally compressed until the ensuing movement of the cross-head I33 had caused the shaft III to rotate in the direction and amount that the lever I2 I had been manually rotated.

If the lever I2I were rigidly connected with the control shaft III instead of being connectedtherewith through the yieldable connection in-- cluding the springs I41, the distance such lever could be moved subsequent to the engagement oi the brake band actuated thereby would depend upon the ensuing speed of movementoi the crosshead I 33 and the speed of the resulting movement of the differential link I56 tending to reestablish the neutral position of the mid-section of this lever. However, by using the yieldable connection between the lever I2! and the control shaft III, the operator can promptly set the lever to any position desired for predetermining the amount of movement of the cross-head I33- which may move at any speed for subsequently reestablishing the radially alined positions of the shaft III and lever I2I illustrated in Fig. 4.

Devices for automatically locking each of the levers I2 I in any set positionalong its quadrant strap I24 and for automatic manual release incident to movement of the knobs are illustrated in Figs. 3 and 5. The lever I24 shown in these two figures can. be seen tohave a pair of strap like extension members I5I secured to the cast portion of the lever and of less width than the cast portion so as to enable the end of such cast portion to form a seat I52 for an end of a compression pring I52 surrounding the extensions I5I. Said extensions [5| straddle their associated quadrant strap I24 and project into a gear holder i5-4 having opposed sections I55 also'stradthing the strap I24. Knob I22 is fastened securely to the upper end of the gear holder I54.- A pair of gears I56 and I5"! are disposed betweenthe holder sections I55 where they are journaled on shafts I58 extending between these sections. The teeth of gears I56 and I51 mesh with one another and are normally pressed into mesh with teeth I55 on the strap I26 by the spring I5 3. So long as both gears I55 and I5? are meshed with the quadrant strap teeth I59, the lever I2! is held against movement. Should the operator grasp the knob I22 and exert pressure thereon for pivoting the lever iZI clockwise as viewed in Fig. 3, the gear holder I54 would be tilted incident to compressing the spring I55 slightly to demesh: the gear I5? from the quadrant strap teeth I55; whereby continued pressure in the clockwise direction on the knob I22 would cause the gear- I56 to roll along the quadrant strap while driving the gear I51 idly. When the Ieve'r has been set at the desired point, the knob I22 will be released whereupon the spring I53 will reestablish the meshed condition of both gears I 56 and I5! with the quadrant strap teeth and prevent accidental displacement of the lever. Counter-clockwise pressure upon the kiiob [2'2 would disengage the gear I56 fIO'nl mesh with the quadrant strap teeth so that the lever could be moved counterclockwise While the gear [51 rotated the gear I55 idly. Upon release of the knob lz'l' the spring I55 would again reestablish the locked position wherein both gears I56 and I 51 mesh with the quadrant strap teeth. This locking ap aratusserves to hold the lever III in any desired position following movement of the lever for compressing the springs I41, Figs. 4 and 5, until the ensuin movement of the; cross-head I 33' has relieved the; tension on the springs I41, thus avoiding the necessity of the operator manually holding the lever I21 in an advanced or retracted osition until. the ensuing movement of the crosshead has relieved such tension on the springs I'4"I'.

In Fig. I it" can be seen that the bearing member IBI for the forward end portion of the drive shaft I8 for the units A and B has the bearing" I62 therein mounted eccentrically with respect to the circular outer peripheral portion I63 of this bearing member that is journale'd in a wall of the" clutch compartment I5. Bearing member ItI has an arm I 64 which, when a, pin I55 therein is pulled rearwardly from within a hole ['65 in the wall of said compartment, can be manipulated for pivoting the bearing member it about the axis I1 and I4 demeshed.

Having thus described a single preferred form of the invention with theview of clearly illustrating the same I claim:

1. In a power transmitting device, a casing, a cross-head bearing extending endwise from said casing, an open-ended tubular driving structure within and journaled in said casing for continuous rotation in one direction coaxially of said cross-head bearing and having its open end disposed toward said bearing, a cross-head recipro cable in said cross-head bearing. an exteriorl y threaded member reciprocable with the crosshead and projecting endwise therefrom into the tubular driving structure, anendwise-constrained rotatable internally threaded member disposed between the driving structure and said cross-' head and having its threads meshed with those of the exterio'rlythreaded member whereby rota-i tion of such internally threaded member in opposite directions causes endwise movement of the exteriorly threaded member and the cross-head in respectively opposite directions, sun' gear means circum'scribing. said driving. structure and". constrained forunidi'rectional rotation therewitlm- J first and second: planetary gear units each com? prising a. ring gear, a carrier and planet gears journaled on said carrier and in driving relation between their respectively" associated ring gear and respective portions of said sungear means;

11 means constraining the carrier of the second unit to rotate in unison with the ring gear of the first unit and with said internally threaded member, and brake means for selectively constraining rotation of the carrier of the first unit or the ring gear of the second unit.

2. in a power transmitting device; a plural part casing having a main part with a principal axis, a controls-containing part spaced radially from said axis, and an intermediate sheet-like part assembled between the first-named parts, said intermediate part having slots in portions thereof projecting interiorly of the casing and spaced axially of the main casing part; a rotatable driving structure mounted coaxially in the main casing part; a driven member mounted in the main casing part for forward or reverse rotation coaxially thereof; planetary drive gearing coaxially in the main casing part and selectively establishable in forward or reverse driving relation between said driving structure and the driven member, said gearing including axially spaced forward and reverse brake drums independently rotatable coaxially of said structure, one of said drums being operable to establish the forward driving relation of the gearing when constrained against rotation in one direction and the other brake drum being operable to establish the reverse driving relation of the gearing when constrained against rotation in the opposite direction, said gearing being neutral to establish neither driving relation when neither drum is constrained; brake bands respectively cooperable with said brake drums, each band having an anchored end portion from which it extends circumferentially of its associated drum in the direction its drum tends to rotate when constrained and having an opposite end portion displaceable in said circumferential direction to frictionally apply such band to its drum to brake the same with a servo action, said brake bands having slots in their end portions; means for anchoring the anchorage ends of said bands to the casing comprising tiltable members each having one end portion projecting into a respective of the anchorage end slots of said bands and each having a second portion projecting into a respective of the intermediate member slots to be held captive thereby while facilitating tilting of such tiltable members so the one portion of each can bear against a side of its associated brake band slot at various positions of adjustment thereof circumferentially of its associated drum, and casing-mounted means manipulatable to regulate the tilt of said tiltable members and hence the position of the anchorage ends of said bands in said zones; and means for selectively applying said bands to their drums comprising a lever pivoted in said casing about an axis parallel with said principal axis and having arms projecting respectively into the slots at the other ends of said bands for selectively applying said bands to their drums when the lever is rotated in respectively opposite directions from a neutral position, a differential link having an intermediate portion connected with said lever to pivot the same from its neutral position in accordance with the direction of displacement of said intermediate portion from a neutral position circumferentially of the lever axis, coaxially rotatable shafts in said controls-containing casing part, means connecting said shafts with respective end portions of said differential link for displacing such end portions in opposite directions circumferentially of the lever axis in accordance with opposite directional rotation of their associated of said shafts, means operably connecting one of said shafts with said driven member to correlate the position of the associated lever end portion with the amount of advance or retraction of said driven member, the other of said shafts being manually operable to displace its associated lever end portion and correspondingly displace the lever intermediate portion from its neutral position while the other end portion reacts against the connecting means therewith to cause selective application of the brake bands in accordance with the direction of manual rotation of said other shaft, and the connecting means at said other end of the lever being operable by the ensuing movement of said driven member to displace said other end portion in the direction to reestablish the neutral position of the intermediate lever portion and of said lever when the driven member is moved an amount correlated with the amount of manual rotation of said other shaft.

3. In a power transmitting device; a rotatable driving structure; a driven member mounted for forward or reverse rotation coaxially with said driving structure; a planetary gearing layout connected between said structure and said driven member and including brake bands for braking respectively associated elements of such gearing to condition the same for driving the driven member in respectively opposite directions from the driving structure, said brake bands having end portions oppositely movable for applying the same in braking relation with their said elements; and control means for said brake bands comprising a lever having arms projecting respectively into operating relation with said ends of the brake bands, said lever being pivotable oppositely from a neutral position wherein neither arm applies its associated brake band and being operable when pivoted in one direction from neutral to cause application of one band and being operable when pivoted in the opposite direction from neutral to cause application of the other brake band, a differential link having an intermediate portion connected with said lever to pivot the same from its neutral position in accordance with the direction of displacement of said intermediate portion from a neutral position thereof circumferentially of the lever axis, coaxially rotatable control shafts, means connecting said shafts with respective end portions of said link for displacing such end portions in opposite directions circumferentially of the lever axis in accordance with opposite directional rotation of their associated of said shafts and to correspondingly displace the intermediate link portion when either end portion opposite to that displaced is constrained against displacement, means operably connecting one of said shafts with said driven member to correlate the position of the associated lever end portion with the amount of advance or retraction of said driven member, the other of said shafts being manually operable to displace its associated lever end portion and correspondingly displace the lever intermediate portion from its neutral position while the other end portion reacts against the connecting means therewith to cause selective application of the brake bands in accordance with the direction of manual rotation of said other shaft, and the connecting means at said other end of the lever being operable by the ensuing movement of said driven member to displace said other end portion in the direction to reestablish the neutral position of the intermediate lever portion and of said lever Number Name Date when the driven member is moved an amount 1,847,693 Kindervater Mar. 1, 1932 correlated with the amount of manual rotation of 1,887,832 Brown Nov. 15, 1932 said other shaft. 1,891,545 Kindervater Dec. 20, 1932 CARL W. MOTT. 5 1,975,835 Farkas Oct. 9, 1934 2,182,386 Patterson Dec. 5, 1939 REFER C CITED 2,283,476 WaibeI May 19, 1942 The following references are of record in the 2,387,713 Bradford 30, 1945 file of this patent: 2,403,092 Lear July 1946 10 2,405,338 Werner Aug. 6, 1946 UNITED STATES PA'I'ENTS Number Name Date OREIGN PATENTS 764,896 Maxim July 12, 1904 Number Country Date 1,790,243 Nilson Jan. 27, 1931 680,748 France May 5, 1930 

